U.S. patent number 4,265,409 [Application Number 06/093,529] was granted by the patent office on 1981-05-05 for web rewinder turret swing control.
This patent grant is currently assigned to Scott Paper Company. Invention is credited to Jon N. Cox, Balbir Singh.
United States Patent |
4,265,409 |
Cox , et al. |
May 5, 1981 |
Web rewinder turret swing control
Abstract
An apparatus that controls the swinging of a frame (50) and the
rotation of a turret (52) in an automatic web rewinding machine.
The frame (50) is pivotally mounted in the machine and a turret
(52) including a plurality of rotatable mandrel assemblies (56) is
mounted for rotation within the frame (50). The control apparatus
includes an indexing device (66) having an output shaft (70) that
undergoes intermittent rotation in response to continuous rotation
of an input shaft (68). One drive means (80), coupled and
responsive to the output shaft (70) of the indexing device (66)
provides intermittent rotation of the turret (52). A second drive
means (78) is provided to control the rotation of the cam (60) in
order to minimize the overlap of the rotation of the cam (60) with
the dwell time of the turret (52). The optimum condition occurs
when the cam (60) rotates only when the turret (52) is indexing and
when the cam (60) does not rotate at all while the turret (52) is
dwelling. This optimum condition is achieved by having the second
drive means (78) also coupled and responsive to the output shaft
(70) of the indexing device (66) for providing the intermittent
rotation of cam (60) in synchronism with the rotation of the turret
(52).
Inventors: |
Cox; Jon N. (Oakland, ME),
Singh; Balbir (Media, PA) |
Assignee: |
Scott Paper Company
(Philadelphia, PA)
|
Family
ID: |
22239433 |
Appl.
No.: |
06/093,529 |
Filed: |
November 13, 1979 |
Current U.S.
Class: |
242/533.5 |
Current CPC
Class: |
B65H
19/2223 (20130101); B65H 2408/23157 (20130101); B65H
2301/4148 (20130101) |
Current International
Class: |
B65H
19/22 (20060101); B65H 019/20 () |
Field of
Search: |
;242/56R,56A,64 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: McCarthy; Edward J.
Attorney, Agent or Firm: Yamaoka; Joseph H. Foley; William
J.
Claims
What is claimed is:
1. An improved automatic web rewinding machine having a pivotally
mounted frame, a turret mounted for rotation within the frame, said
turret including a plurality of rotatable mandrel assemblies, means
including a rotating cam for controlling the angular position of
the frame, and index means for intermittently rotating the turret
wherein the improvement comprises means for intermittently rotating
the cam so that a major portion of the cam rotation coincides with
the rotation of the turret.
2. An improved web rewinding machine as recited in claim 1 wherein
the means for controlling the angular position of the frame
comprises a rotating cam mounted on the frame and a roller fixedly
mounted in the rewinding machine.
3. An improved web rewinding machine as recited in claim 1 wherein
the means for intermittently rotating the cam is a timed
clutch.
4. An improved web rewinding machine as recited in claim 1, wherein
the means for intermittently rotating the cam is an indexer.
5. An improved web rewinding machine as recited in claim 1 wherein
the cam is stationary when the turret is stationary and the cam
makes one complete revolution as the turret indexes whereby the
entire periphery of the cam is available to control the swinging of
the frame while the turret is indexing.
6. An improved web rewinding machine as recited in claim 1 wherein
the index means is mounted on the frame.
7. An improved web rewinding machine as recited in claim 2 wherein
the cam is stationary when the turret is stationary and the cam
makes one complete revolution as the turret indexes whereby the
entire periphery of the cam is available to control the swinging of
the frame while the turret is indexing.
8. An improved web rewinding machine as recited in claim 7 wherein
the index means is mounted on the frame.
9. An improved automatic web rewinding machine having a bedroll, a
pivotally mounted frame, a turret mounted for rotation within the
frame, said turret including a plurality of rotatable mandrel
assemblies, a cam mounted for rotation within the frame, a roller
mounted in the rewinding machine and coacting with the cam to
control the position of a mandrel with respect to the bedroll,
wherein the improvement comprises:
(a) an index means having an output shaft that undergoes
intermittent rotation in response to continuous rotation of an
input shaft of the index means;
(b) first drive means for continuously rotating the input shaft of
the index means;
(c) second drive means, responsive to the output shaft of the index
means, for providing intermittent rotation of the turret; and
(d) third drive means, also responsive to the output shaft of the
index means, for providing intermittent rotation of the cam thereby
controlling the swinging of the frame.
10. An improved automatic web rewinding machine as recited in claim
9 wherein the index means is a timed clutch.
11. An improved web rewinding machine as recited in claim 9 wherein
the cam is stationary when the turret is stationary and the cam
makes one complete revolution as the turret indexes whereby the
entire periphery of the cam is available to control the swinging of
the frame while the turret is indexing.
12. In an automatic web rewinding machine having a pivotally
mounted frame, a turret mounted for rotation within the frame, said
turret including a plurality of rotatable mandrel assemblies, and
means, including a rotating cam for controlling the angular
position of the frame, an improved apparatus for controlling the
rotation of the turret and the swinging of the frame
comprising:
(a) an index means having an output shaft that undergoes
intermittent rotation in response to continuous rotation of an
input shaft of the index means;
(b) first drive means for continuously rotating the input shaft of
the index means;
(c) second drive means, responsive to the output shaft of the index
means, for providing intermittent rotation of the turret; and
(d) third drive means, also responsive to the output shaft of the
index means, for providing intermittent rotation of the cam thereby
controlling the swinging of the frame.
13. An apparatus as recited in claim 12 wherein the index means is
a timed clutch.
14. An apparatus as recited in claim 12 wherein the cam is
stationary when the turret is stationary and the cam makes one
complete revolution as the turret indexes whereby the entire
periphery of the cam is available to control the swinging of the
frame while the turret is indexing.
15. In an automatic web rewinding machine having a pivotally
mounted frame, a turret mounted for rotation within the frame, said
turret including a plurality of rotatable mandrel assemblies, and
means including a rotating cam for controlling the angular position
of the frame, an improved apparatus for controlling the rotation of
the turret and the swinging of the frame comprising:
(a) an index means having an output shaft that undergoes
intermittent rotation in response to continuous rotation of an
input shaft of the index means;
(b) first drive means for continuously rotating the input shaft of
the index means;
(c) second drive means, responsive to the output shaft of the index
means, for providing intermittent rotation of the turret;
(d) a second index means having an input shaft continuously driven
by the first drive means and having an output shaft that undergoes
intermittent rotation; and
(e) third drive means responsive to the output shaft of the second
index means for providing intermittent rotation of the cam thereby
controlling the swinging of the frame.
16. An improved apparatus as recited in claim 15 wherein the second
index means is a timed clutch.
17. An apparatus as recited in claim 15 wherein the cam is
stationary when the turret is stationary and the cam makes one
complete revolution as the turret indexes whereby the entire
periphery of the cam is available for control the rotation of the
frame while the turret is indexing.
Description
TECHNICAL FIELD
This invention is generally related to automatic web rewinding
machines wherein a web from a large roll, known in the art as a
parent roll, is automatically wound onto cores to form smaller
rolls having a diameter and length that is suitable for use by a
consumer. More particularly, this invention is related to automatic
web rewinding machines that have a rotating turret mounted on a
swinging frame. This invention is specifically directed to an
apparatus for simultaneously controlling the swinging of the frame
and the rotation of the turret.
BACKGROUND ART
The Series 100 and 150 continuous winders manufactured by Paper
Converting Machine Company and as described in U.S. Pat. Nos.
2,769,600--Kwitek et al and 3,179,348--Nystrand et al are
representative of the prior art. Those automatic web rewinding
machines have a turret mounted for rotation within a frame which is
pivotally mounted in the machine. The turret includes six rotatable
mandrel assemblies. The web being rewound from a parent roll passes
over a bedroll of the machine and is wound about a core placed on a
mandrel assembly located at a winding station adjacent to the
bedroll. A fresh core, with glue applied to the core, is mounted on
the mandrel assembly that will next approach the winding station.
As the winding of the roll at the winding station nears completion,
the turret begins to index, or rotate, and the frame is caused to
swing toward the bedroll so that the fresh core is brought into
close proximity to the bedroll. The web is then severed and the
free end of the web from the parent roll is caused to be
transferred to the glue on the fresh core to begin the winding of a
roll on the fresh core. Immediately after transfer, the turret
swings away from the bedroll so that the roll being wound does not
contact the bedroll. Before the turret finishes indexing it is
necessary to swing the turret to a dwell position at which the next
fresh core which has glue freshly applied to it; will not
prematurely contact the web during the winding process. After the
turret has completed indexing, or rotating 60 degrees, it dwells in
that position for a considerable period of time during which a
completely wound roll can be stripped from a mandrel assembly
located adjacent to a stripping station and a fresh core can be
placed onto a mandrel assembly that is located adjacent to a supply
of cores.
In the prior art machines, the swing of the frame and turret
assembly is controlled by a cam mounted for rotation on the frame
which cooperates with a roller assembly mounted in the machine. As
the cam rotates, the periphery of the cam controls the angle of
rotation of the frame and, therefore, the location of the freshly
glued core with respect to the web being wound and the bedroll. In
the prior art machines, an internal Geneva mechanism is used to
control the indexing of the turret. The internal Geneva mechanism
has an input shaft and an output shaft, and for one continuous
revolution of the input shaft, the output shaft dwells 33 percent
of the time and causes the turret to rotate through 1.05 radians
during the remainder of the time. In the prior art machines, the
cam is geared to the input shaft to the internal Geneva mechanism
so that it makes one continuous revolution for each indexing cycle
of the turret. Since it is only desired to swing the turret while
it is indexing, 33 percent of the cam surface is not available to
control the swinging of the turret.
Attempts have been made to increase the productivity of the prior
art automatic web rewinding machines by running them at a higher
cycle rate. When operated at these higher cycle rates, it has been
found that the reduced dwell time of the turret is insufficient to
reliably strip a completely wound core from the mandrel assembly,
or to place a fresh core onto a mandrel assembly. Another problem
that is encountered at the higher cycle rate is increased vibration
and backlash of the turret which sometimes causes poor transfers of
the web to the fresh core or tearing of the web during the winding
of the roll. This increased vibration and backlash is caused by
high pressure angles at the point of contact of the cam periphery
and the roller. It was believed that a more effective transfer of
the web to the fresh core would take place if the transfer occurred
"higher up on the bedroll", which occurs by swinging the turret
further toward the bedroll at transfer so that the vertical
distance between the axis of the mandrel that is approaching the
winding station and the axis of the bedroll is increased over that
of the prior art machines. Normally this would be accomplished by
shaping the cam so that the frame and turret assembly undergo the
desired additional motion toward the bedroll. However, when it was
attempted to design a cam to provide this additional rotation of
the frame and turret assembly, it was found that the cam could not
be physically realized because such a cam would be "under cut".
Another prior art automatic web rewinding machine is the series 200
continuous winder manufactured by Paper Converting Machine Company.
In this machine, the intermittently rotating turret is mounted in a
stationary frame. As in the case of the series 100 and 150
rewinding machines, during the indexing of the turret, it is
necessary to prevent the fresh core with the glue applied thereto
from coming in contact with the web that is being wound. This is
accomplished by means of a moving deflector bar, driven in
synchronism with the turret, which causes the web to be deflected
toward and in close proximity to the bedroll which keeps the web
out of the path of the freshly glued core. Although the series 200
automatic web rewinding machine, which operates at a higher cycle
rate than the series 100 and 150 machines is commercially
available, the increase in productivity does not justify the
purchase of a new machine to replace the swinging turret model. It
is also not economically feasible to modify the swinging turret
machines to have a fixed turret frame and to incorporate a web
deflector bar.
DISCLOSURE OF INVENTION
In accordance with this invention, the apparatus that controls the
swinging of the frame and the rotation of the turret in an
automatic web rewinding machine includes an indexing device having
an output shaft that undergoes intermittent rotation in response to
continuous rotation of an input shaft. One drive means, coupled and
responsive to the output shaft of the indexing device, provides
intermittent rotation of the turret. Since it is only desired to
swing the frame and turret assembly when the turret is indexing, a
second drive means is provided to control the rotation of the cam
in order to minimize the overlap of the rotation of the cam with
the dwell time of the turret. The optimum condition occurs when the
cam rotates only when the turret is indexing and when the cam does
not rotate at all while the turret is dwelling. Under this optimum
condition of turret swing control, the entire periphery of the cam
is available to control the swinging of the frame. This optimum
condition is achieved by having the second drive means also coupled
and responsive to the output shaft of the indexing device for
providing the intermittent rotation of the cam in synchronism with
the rotation of the turret.
The time available during the dwell time of the turret at higher
cycle rates is increased by replacing the internal Geneva mechanism
used in the prior art machine, which has a dwell-to-index ratio of
1 to 2, by an indexing device that has a dwell-to-index ratio of 1
to 1. The combined factors of changing the dwell-to-index ratio,
rotating the cam only when the turret is indexing and operating at
a higher cycle rate all result in the critical portion of the
swinging of the frame taking place over about 1.22 radians of
rotation of the cam as compared to about 0.523 radians of rotation
of the cam for the prior art machines. As a result, the pressure
angles of the roller and cam arrangement are reduced considerably
and the operation of the automatic web rewinding machine is
considerably smoother, particularly during transfer of the web to a
fresh core, even though it is operating at a higher cycle rate.
BRIEF DESCRIPTION OF DRAWINGS
While the specification concludes with claims particularly pointing
out and distinctly claiming that which is regarded as the present
invention, the objects and advantages of this invention can be more
readily ascertained from the following description of a preferred
embodiment when read in conjunction with the accompanying drawings
in which:
FIG. 1 is a side elevation, partially in block diagram form, of
portions of the automatic web rewinding machine including the
turret swing control apparatus.
FIG. 2 is a side view, partially in block diagram form, of a prior
art turret swing control apparatus.
FIG. 3 is a side view, partially in block diagram form, of another
embodiment of a turret swing control apparatus in accordance with
this invention.
FIG. 4 is a block diagram showing independent index means for
controlling the cam.
FIG. 5 is a diagram showing particular means for driving the turret
and the cam.
BEST MODE FOR CARRYING OUT THE INVENTION
For the sake of convenience, an element depicted in more than one
figure will retain the same element number in each figure. FIG. 1
shows the turret swing control apparatus of this invention and
those portions of an automatic web rewinding machine necessary or
helpful in disclosing the invention. A more detailed description of
an automatic web rewinding machine having a swinging turret which
can be controlled in accordance with this invention can be found in
U.S. Pat. No. 2,769,600, issued to E. M. Kwitek et al, which is
hereby incorporated by reference into this application. Referring
now to FIG. 1, there is shown a parent roll 10 of a web material
such as paper tissue. A shaft 12 extends through the parent roll
10. Each end of shaft 12 is supported by an elongated slot 18
formed within a pair of spaced-apart brackets 14. The brackets 14
are supported on a base or floor by a suitable supporting structure
16 which rests on the machine base and which can also be secured to
the main frame 46 of the machine. Slots 18 slope downward toward
the machine so that the gravitational force acting on the parent
roll 10 causes it to move downwardly in the slots 18 until the
periphery of the parent roll 10 contacts a delivery roller 20. The
delivery roller 20 is journalled upon suitable bearings in the
supporting structure 16 and is driven so that upon frictional
engagement with the parent roll 10, a web 22 is delivered from the
parent roll 10 to the winding machine. The web 22 is delivered
upwardly over an idler roller 26 which is rotatably mounted in a
bracket 24 secured to main frame 46 of the machine. The web 22 then
travels over another idler roller 28 mounted in the rewinding
machine, through a nip formed by a driven feed roll 30 and a
secondary perforator roll 32, and then through a nip formed by the
secondary perforator roll 32 and a primary perforator roll 34. The
primary perforator roll 34 is equipped with a plurality of spaced
perforating knives 36 that coact with recesses 38 in the secondary
perforator roll 32 to provide spaced apart transverse perforations
of the web 22. The web 22 then travels between a nip formed by the
secondary perforator roll 32 and a secondary slitting roll 40 where
the web 22 is slit longitudinally into predetermined widths by the
coaction of the secondary slitting roll 40 with slitting knives 42
carried on a shaft 41. After the web 22 has been slit, it passes
through a nip formed by the secondary slitting roll 40 and a
bedroll 44 which is secured to a shaft 43. The web 22 is then
carried over the bedroll 44 and is wound upon cores (not shown)
which are mounted on rotatable mandrel assemblies 56a through 56f
mounted in a turret 52. The turret assembly 52 is keyed to a turret
shaft 54 which is rotatably mounted in a frame member 50 and, as
shown in the figure, the six mandrel assemblies 56a through 56f are
equiangularly spaced about the turret shaft 54. As shown in FIG. 1,
mandrel assembly 56b is in the vicinity of the winding station
where web 22 is wound onto a core placed on mandrel assembly 56b;
mandrel assembly 56c is adjacent to a stripping station where a
completed roll is removed from mandrel assembly 56c; and mandrel
assembly 56d is adjacent to a core receiving station where a fresh
core is placed onto mandrel assembly 56d. As the turret 52 rotates
clockwise, as indicated by arrow 57, to bring a fresh core to the
position of mandrel assembly 56a, glue is applied to the surface of
that core. In order to facilitate the transfer of the web 22 to the
glued core on mandrel assembly 56a, the frame 50 in which the
turret 52 is mounted can rotate about a pivot shaft 48. Secured to
the frame 50 is a counterweight 82 which tends to rotate the frame
50 toward the bedroll 44. Cam 60, which is keyed to a shaft 58 that
is rotatably mounted within the frame 50, cooperates with roller
member 62 mounted in bracket 64 in the machine to control the
desired position of frame 50 with respect to bedroll 44. As cam 60
is caused to rotate, the shape of the cam 60 controls the position
of mandrel assemblies 56a and 56b with respect to the bedroll
44.
One approach for controlling the rotations of turret 52 and cam 60
is shown in FIG. 2 and is described in detail in the aforementioned
patent to Kwitek et al. The primary drive means as indicated by
block 72 provides a continuously rotating shaft 74 output. Drive
means 76, indicated schematically as a dashed line, connects output
shaft 74 with an input shaft 68 of an internal Geneva mechanism 66.
The input shaft 68 continuously rotates at a rate of one revolution
per winding cycle of the machine. For each revolution of input
shaft 68, an output shaft 70 of the internal Geneva mechanism 66
remains stationary for one-third of a cycle and rotates 60 degrees
during the remaining two-thirds of the cycle. Although the turret
shaft 54 is depicted as being driven from the output shaft 70 by
drive means 80, indicated schematically by a dashed line, and the
shaft 58 to which cam 60 is fastened is shown as being driven from
continuously rotating output shaft 74 by drive means 86, also
represented schematically by a dashed line, as described in the
patent to Kwitek et al, the cam 60 is geared to the input shaft 68
of the internal Geneva mechanism 66 and the turret 52 is keyed to
the output shaft 70 of internal Geneva mechamism 66. When driven in
this manner, the cam 60 continuously rotates both during the dwell
time of the turret 52 and during the indexing of the turret 52.
Since it is not desired to swing the frame 50 and turret 52 while
the turret 52 is dwelling, thirty-three percent of the periphery of
the cam 60 is of a constant radius and is unavailable to control
the swinging of the frame 50 and turret 52.
Referring now to FIG. 1, the apparatus for controlling the rotation
of cam 60 and turret 52 in accordance with the invention will now
be described. An indexing device 66 is shown mounted on the frame
50. The indexer 66 has an input shaft 68 which is driven from the
continuously rotating shaft 74 of the primary drive 72 by drive
means 76 shown schematically as a dashed line. The input shaft 68
of the indexer 66 is continuously driven through one revolution for
each cycle of the machine. In one preferred embodiment of the
invention, the output shaft 70 of the indexer 66 remains stationary
for one-half of a cycle and undergoes 62.8 radians of rotation
during the second half of the cycle. Drive means 80, shown
schematically as a dashed line, is responsive to the rotation of
output shaft 70 and causes the turret shaft 54 to rotate 1.05
radians during each machine cycle. Drive means 78, indicated
schematically as a dashed line, is also responsive to the rotation
of output shaft 70 and causes shaft 58, to which cam 60 is
fastened, to rotate 6.28 radians while the output shaft 70 is
rotating and causes the shaft 58 to be stationary when the output
shaft 70 is stationary.
FIG. 3 illustrates substantially the same arrangement for
controlling the rotation of turret shaft 54 and cam shaft 58 as
depicted in FIG. 1 except that the indexer 66 is not mounted on the
frame 50.
The optimum control of the rotation of cam 60 occurs when the cam
60 is stationary when the turret 52 is stationary, and begins to
rotate precisely when the turret 52 begins to index and completes
one complete revolution precisely when the turret 52 stops
rotating, because under these conditions, the entire periphery of
the cam 60 is available to control the swinging motion of the frame
50 and turret 52. This optimized swing control can be achieved with
the cam and turret control means illustrated in FIG. 1, 3, 4, or
5.
The cam drive arrangement in FIG. 4 illustrates another embodiment
of the invention which can be used if it is not desired to have the
rotation of the cam 60 be in precise synchronism with the rotation
of the turret 52. A first indexing device 66 controls the rotation
of the turret shaft 54 and a second indexing device 88 controls the
rotation of cam shaft 58. Drive means 76a, indicated schematically
as a dashed line, responds to the continuous rotation of shaft 74
and provides continuous rotation of input shaft 90 of index means
88. Drive means 78, indicated schematically as a dashed line,
responds to the intermittent rotation of output shaft 92 and
provides for intermittent rotation of cam shaft 58.
Referring now to FIG. 5, there is depicted a preferred embodiment
for driving the input shaft 68 of the indexer 66 and for driving
the cam shaft 58 and the turret shaft 54 from the output shaft 70
of indexer 66. The indexer 66 is a Cyclo-Index mechanism, Model
180-1-2800, which is available from the Hilliard Corporation, 100
West 4th Street, Elmira, N.Y. 14902. The indexer 66 is mounted on
the frame 50 as shown in FIG. 1. A sprocket 94 is secured to the
continuously rotating shaft 74 of the drive means 72. A sprocket 98
is secured to the input shaft 68 of the indexer 66. The drive for
sprocket 98 is obtained from sprocket 94 by means of a chain 96.
The tensioning member 100 compensates for the changing distance
between the axis of shaft 74 and the axis of shaft 68 that occurs
when the indexer 66 is mounted on the swinging frame 50. The drive
means 72, continuously rotating shaft 74, sprocket 94, chain 96 and
sprocket 98 together comprise means for continuously rotating the
shaft 68 of the indexer 66. A sprocket 102 having 21 teeth is
fastened to the output shaft 70 of the indexer 66. A similar
sprocket 106 also having 21 teeth is secured to the cam shaft 58. A
sprocket 110 having 42 teeth is fastened to a counter shaft 108.
Also secured to the counter shaft 108 is a gear 112 having 26
teeth. Gear 112 meshes with gear 114 which has 78 teeth and which
is fastened to the turret shaft 54. The drive for both sprockets
106 and 110 is obtained from the output shaft 70 by means of chain
104. Since sprockets 102 and 106 both have the same number of
teeth, one complete revolution of output shaft 70 will result in
one complete revolution of cam shaft 58. Sprocket 102, chain 104
and sprocket 106 together comprise drive means responsive to the
output shaft 70 of the indexer 66 for providing intermittent
rotation of the cam 60. Since sprocket 110 has twice as many teeth
as sprocket 102, one revolution of output shaft 70 will result in
3.14 radians of rotation of counter shaft 108 and since gear 114
has three times as many teeth as gear 112, 180 degrees of rotation
of counter shaft 108 results in 1.05 radians of rotation of turret
shaft 54. Thus, it can be seen that for one complete revolution of
the output shaft 70 of the indexer 66, the cam 60, which is secured
to cam shaft 58, will undergo one complete revolution as the turret
is indexed through 1.05 radians of rotation. Sprocket 102, chain
104, sprocket 110, gear 112, and gear 114 together comprise drive
means responsive to the output shaft 70 of the indexer 66 for
providing intermittent rotation of the turret 52. When the cam 60
and the turret 52 are controlled in this manner, the entire
periphery of the cam 60 is available to control the swinging of the
frame 50 and the turret 52. This represents a 50 percent increase
over the prior art in the amount of the periphery of cam 60 to
control the swinging of frame 50 and turret 52. As a result, the
pressure angles between cam 60 and roller 62 are significantly
reduced, and, furthermore, in contrast to the prior art machines,
it is possible to physically realize a cam 60 that will allow
transfer to occur higher up on the bedroll. This is illustrated in
FIG. 1 which shows a typical point 118 representing the location of
the periphery of a fresh core at transfer for the prior art
machines and a point 120 representing the location of the periphery
of a fresh core at transfer that is "higher up on the bedroll" in
accordance with this invention. Using as a reference a horizontal
line 116 passing through the axis of the bedroll shaft 43, the
point 118 is typically about 0.004-0.007 meters from the surface of
the bedroll 44 and makes an angle, A, of about 0.262 radians with
horizontal line 116. It was not possible to physically realize a
cam to provide an angle, A, much greater than 0.262 radians. The
point 120 representing the location of the periphery of a fresh
core at transfer in accordance with this invention is about
0.004-0.007 meters from the surface of the bedroll 44 and makes an
angle, B, of about 0.384 radians with the horizontal line 116 which
allows more efficient transfer of the web to a fresh core.
While the present invention has been described with reference to a
specific embodiment thereof, it will be obvious to those skilled in
the art that various changes and modifications may be made without
departing from the invention in its broader aspects. For example,
since the index means 66 is a device that converts continuous shaft
rotation into intermittent shaft rotation, a timed clutch can be
utilized to accomplish the function.
* * * * *